Air conditioning apparatus

ABSTRACT

An air conditioning apparatus wherein a portion of the air is removed from the conditioned space and sprayed with water, the resulting humidified air is conducted through a decreasing volume first chamber, the first chamber being in a heat transfer relationship with an increasing volume second chamber, air from the conditioned space is passed through the second chamber in an opposite direction to the passage of air through the first chamber.

United States Patent [191 Manning 1 'July 2, 1974 AIR CONDITIONING APPARATUS [76] Inventor: Ernest Alan Manning, 6564 Valley Circle Blvd, Canoga Park, Calif. 91304 [22] Filed: Apr. 5, 1972 [21] App]. No.: 241,306

[52] U.S. Cl. 165/60, 165/122 [51] Int. Cl F24f 3/14 [58] Field of Search l65/l66.66, 122, 60, 102

[56] References Cited UNITED STATES PATENTS 1,409,520 3/1962 Bird 165/64 2,019,351 10/1935 Cathron 165/66 Primary Examiner-Charles Sukalo Attorney, Agent, or Firm-Robert E. Geauque 57 5 ABSTRACT An air conditioning apparatus wherein a portion of the air is removed from the conditioned space and sprayed with water, the resulting humidified air is conducted through a decreasing Volume first chamber, the first chamber being in a heat transfer relationship with an increasing volume second chamber, air from the conditioned space is passed through the second chamber in an opposite direction to the passage of air through the first chamber.

18 Claims, 5 Drawing Figures mamzmm 21914 3821982 sum 1 or 2 i Fig.

SHEET 2 OF Fig. 2. /IO

BACKGROUND OF THE INVENTION The apparatus of the present invention is within the field of air conditioning apparatuses and more particularly to an air conditioning apparatus whose primary function is to effect cooling of a conditioned space. The conditioned space is to be defined as usually an enclosure, but in some cases it may be an open region, as an operators fixed working position in a hot industry. or a partially open region such as an unroofed patio or lobby.

The most common type of cooling apparatus is the mechanical refrigeration air conditioning unit employing a low boiling point type of refrigerant (such as Freon 12) which is recirculated within the apparatus by means of a motor driven compressor located in a closed-loop system, between an evaporator (placed in the air ducting) and a condenser located on the outside to dissipate the heat. This type of system is comparatively complex, having expensive components which contribute to high initial cost. These systems consume considerable amounts of power, with resulting high operating expense.

The evaporative cooler is quite low in initial cost by comparison with a mechanical refrigeration unit and is also inexpensive to operate. However, evaporative coolers have several severe drawbacks, and these are roughly as follows:

a. Their ability to remove heat from the conditioned space is radically reduced when the relative humidity of the ambient air is high.

b. They depend upon 100 percent air change under all conditions; that is to say, air must be drawn in from the outside through the unit into the conditioned space, and then pass directly to the outside again. This air must have high velocity to get the most out of the cooling effect, resulting in clammy and uncomfortable conditions most of the time.

c. Water economy poor; heavy discharge of water vapor to atmosphere when running no recon.- densation (recovery) within the unit.

If an air conditioning apparatus could be employed which combined the merits of the evaporative cooler (low initial cost and reduced power consumption) with the merits of the conventional mechanical refrigeration type air conditioner with its ability to remove moisture from the air (remove latent heat) and also lower the temperature (removal of sensible heat), such a unit would be within the financial reach of small businesses and other people who at present have to live and work in industry under quite severe conditions of heat, high humidity and relatively poor air circulation for a large part of the year (particularly in the South Western regions). It is the primary object of the apparatus of this invention to accomplish this objective.

SUMMARY OF THE INVENTION The air conditioning apparatus of this invention employs the use of an electric motor which rotatably drives an impeller. The impeller is to conduct air within a first chamber and also to conduct air within a second chamber. The volume of air which goes into the first chamber is significantly less than the volume of air being conducted into the second chamber. The air which is conducted into the first chamber is sprayed with water, a portion of this water becoming vaporized, to commence a heat transfer process inwhich heat is removed from this air within the first chamber. As the air is conducted through the first chamber, it continues to take heat from the wall separating the first and second chamber, and disposing of this heat in the form of continued vaporization of the water droplets. This heat transfer process continues to the point where recon densation begins; upon entry to the water recovery plenum. Upon entering this plenum a rapid reduction in both velocity and pressures of this mixture takes place. to cause recondensation of the vapor. As the air is con ducted through the second chamber, the direction of airflow through the second chamber is opposite to the direction of air flow within the first chamber. As the air is conducted through the second chamber, the air expands, and in a regulated manner, due to the second chamber being on the low pressure side of the impeller fan, and to the chamber increasing in volume relative to the flow of air. Because of the relationship between the first and second chambers, heat energy is readily transmitted therebetween.

The primary feature of this invention is to design an air conditioning apparatus wherein a unique method is employed to combine existing evaporative cooling techniques, and existing counter-flow cooling tech niques, by the utilization of conical, or other shaped surfaces of revolution to influence the behavior of the air passing therebetween, and wherein a portion of the air is removed from the conditioned space'and sprayed with water, the resulting humidified air is conducted through a decreasing volume first chamber.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an overall view of the air conditioning apparatus of this invention;

FIG. 2 is a cross-sectional view of the apparatus of this invention taken along line 2-2 of FIG. 1;

FIG. 3 is a fragmentary cross-sectional view of a portion of the apparatus of this invention taken along line 3-3 of FIG. 2;

FIG. 4 is a schematic diagram of the air flow through the apparatus of this invention; and

FIG. 5 is a partly cross-sectional view of a modified form of air conditioning apparatus of this invention.

DETAILED DESCRIPTION OF THE SHOWN EMBODIMENT Referring particularly to the drawings, there is shown in FIG. 1 the air conditioning apparatus 10 of this invention which is to operate in conjunction with an exhaust stack 12. The apparatus 10 is designed to extract air from a conditioned space, not shown, and conduct such into a first inlet 14 and a second inlet 16. Air is to be conducted into the exhaust stack 12 and then emitted into the ambient.

An electric motor 18 is fixedly mounted by attachment means 20 upon a plate 22. The motor 18 is to be supplied electrical energy from a source (not shown). Motor 18 causes operation of a shaft 24 which in turn rotationally drives a pulley 26. The pulley 26 drives pulley 28 which is connected through a belt 30. A shaft 32 is connected to the pulley 28 and is rotated thereby. Another pulley 34 is secured upon the shaft 32.

The free end of the shaft 32 is connected to a pump 36. The function of the pump 36 will be explained further on in the specification. A belt 38 cooperates with the pulley 34 and effectsrotation of shaft 40. Shaft 40 is rotationally mounted by bearing assembly 42 within plate 22. The free end of the shaft 40 is rotationally mounted by a bearing assembly 44 within a second plate 46. The free end of the shaft 40 is secured to an impeller hub 48.

Extending radially outwardly from the impeller hub 48 are a plurality of fan blades 50. The fan blades 50 are to conduct air through the first inlet 14, through openings 52 located within the plate 46 and into a cooling plenum 54. Also, a small portion of the air moved by the fan blades 50 is conducted interiorly of the shaft 40 and is adapted to pass about the motor 18. This small portion of air is to effect cooling ofthe motor 18 and prevent overheating of such. The air, after passing about the motor 18, is conducted into exhaust stack 12 by means of an interior exhaust stack 56. The exhaust stack 56 is fixedly mounted by a plate 58 to an interior shell 60. The interior shell 60 is shown cone-shaped, the function of which will be described further on in the specification.

The air which is located within the plenum 54 is conducted through ports 62 within the plenum 54 into the inlet of a first chamber 64. The first chamber 64 basically comprises an annular space between the interior shell 60 and an intermediate shell 66. The first chamber 64 has an outlet 68 which communicates with a moisture recovery plenum 70. it is to be noted that the first chamber 64 steadily decreases in volume from its inlet to the outlet 68. The location ofthe intermediate shell 66 in this example is such so as to be equidistantly spaced from the interior shell 60.

Surrounding the fan blades 50 and spaced a small distance therefrom is a fan housing 72. Connected to the fan housing 72 and extending radially outwardly therefrom are a plurality of support arms 74. Secured to the support arms 74 are a plurality of impeller blades 76. The impeller blades 76 are to cause movement of air through outlet 78. The air is supplied to the outlet 78 from a second chamber 80. Second chamber 80 is similar to the first chamber 64 in shape and is formed be tween the intermediate shell 66 and an outer shell 82. The chamber 80 has an inlet 84 which is located adjacent the second inlet 16. Air is to be conducted through the second inlet 16 by means of the suction action created by the rotating of the impeller blades 76 and is conducted through the second chamber 80 and discharged through outlet 78.

The pump 36 is submerged within a reservoir 86. The reservoir 86 is to include therein a supply of water 88. While it is envisioned that water 88 will be contained within the reservoir 86, it is considered to be within the scope of this invention to employ another fluid which has properties similar to water. The reservoir 86 is annular in configuration and is substantially concentric to the shaft 40 except for an extension 90. The pump 36 is to be located within the extension 90.

The pump 36 includes means, not shown, for moving the water 88 through conduit 92. The conduit 92 is connected to a ring 94. The ring 94 is located within the inlet to the first chamber 64. The ring 94 includes a plurality of closely, spaced-apart apertures 96. The water 88 which is conducted into the ring 94 is ejected by the pressure from the pump 36 through the apertures 96 into the first chamber 64. This ejecting of the water produces a very fine misty spray of water into the first chamber 64.

The'function of the water being ejected into the first chamber 64 is to effect a humidifying of the air within the first chamber 64. It is desired that a significant amount of the water ejected into the air within the first chamber 64 will be evaporated. As the air moves along the first chamber 64, a portion of this water may condense and it is actually envisioned that within the moisture recovery plenum a significant amount of the water will be condensed. The condensed water is permitted to run freely along the interior shell 60 and the intermediate shell 66 back into the reservoir 86. it is to be understood that the water within the reservoir 86, upon reaching a certain low level, will be replenished from a source (not shown). Also, this replenishment will probably be accomplished automatically.

The moisture recovery plenum 70 is encased by an annular housing 98. The interior portion of the housing 98 then communicates directly into the interior of the stack 12. The outer surface of the housing 98 is located directly adjacent the inlet 16.

In discussing the thermodynamic operation of the apparatus of this invention, reference should be had in particular to FIG. 4 of the drawings. Upon activation of the motor 18, the impeller blades 76 and the fan blades 50 are rotatably driven. As a result, a first quantity of air is being conducted through inlet 14 into the first chamber 64. Simultaneously therewith, a second quantity of air is being sucked into the inlet 16 and into the second chamber 80. The properties of the air within the first chamber 64 are significantly changed by the spraying of the water by means of the spray ring 94 adjacent the inlet of the first chamber 64. The pump 36, to supply the water to the ring 94, is activated by the power supplied by motor 18. The water spray is continuously ejected into the first quantity of air entering the chamber 64 while the motor 18 is operating. Evaporation of a portion ofthis moisture occurs which produces an immediate reduction in the temperature of the first quantity of air entering the first chamber 64.

As is readily apparent from the drawing, first chamber 64 is wider at the base than at the apex. As the air enters chamber 64 it is at a lower pressure because of the restriction at the ports. The effect of this pressure drop is to cause evaporation to take place more readily than if it were at a higher pressure. Also, the velocity of this mixture through the chamber 64 is at its lowest in the region of the source of the water spray. The surface area of the intermediate shell 66 is also at its greatest here. This permits the apparatus 10, when operating as a cooler to transfer more heat away from the conditioned space.

The size of the outlet 68 of chamber 64 has an impor tant relationship to the size of the entry ports 62, that is to say, the outlet 68 also acts as a restricting orifice. If the chamber 64 was of uniform size, an abrupt interruption of flow would occur as the mixture approached the outlet 68. However, since the outlet is formed at the apex or narrow end of chamber 64, the velocity of the mixture increases more or less uniformly as it travels through chamber 64, and exits chamber 64 without interruption. The pressure drop normally associated with this type of velocity increase helps sustain the vaporization process throughout the length of chamber 64, so that heat is more easily absorbed.

The chamber is on the low pressure or suction side of impeller 76, and as the conditioned air is being conducted through chamber 80, it is moved continually into a greater volume. As a result, an expansion of the conditioned air takes place, along with a decrease in velocity. This results in facilitating the emission or removal of heat from the medium. Because of the high thermal conductivity in the intermediateashell 66 and the large area thereof due to the conical configuration, this heat is readily transferred through the wall 66 and absorbed by the medium within the first chamber 64. This is the primary mode of heat removal. However, secondary modes of heat removal are also employed through condensation.

One of the secondary modes is as follows: It is desired, when the apparatus is operating as a cooler, to lower the temperature of the air as it passes through the second chamber 80. One way in which this occurs is that the dry bulb temperature of the air passing through the chamber 80 will be lowered sufficiently below dew point due to the decrease in pressure while passing through the expansion chamber 80. This will result in condensation (latent heat removal) andeventual removal of the moisture within the chamber 80 by permitting the moisture to run down the, sides of the chamber 80 into a collecting chamber, not shown, and eventually be conducted into reservoir 88. The heat that is emitted in effecting the removal of the moisture within the chamber 80 is transmitted through the intermediate shell 66 and is absorbed by the moisture-laden air within chamber 64.

The quantity of air passing through chamber 64 is substantially less than the quantity of air passing through chamber 80. However, the air within chamber 64 is capable of absorbing a substantial amount of heat because of the changed properties of the air within chamber 64 due to the inclusion of moisture by means of the spray ring 94. It is actually envisioned that the quantity of air passing through chamber 64 would only be approximately one-tenth to one-twentieth of the volume of the air passing through chamber 80 unless the apparatus is set up for rapid removalof contaminated atmosphere in specific industrial installations whereby this contaminated atmosphere undergoes a scrubbing" action as it passes through thespray chamber, thus releasing only clean air to the atmosphere.

A further secondary mode is as follows:

The condensation of the water vapor within the chamber 80 is facilitated by the vortex action created by the action of the rotating impeller blades 76. This action significantly assists in the removal of latent heat from the air passing through chamber 80. i

Either or both of the above described modes may be operative to a lesser or a greater extent to lower the temperature passing through chamber 80, depending upon the ambient conditions. For example, having anibient conditions of high temperature and very low relative humidity, most of the cooling load is expected to be carried by the evaporative cooling section of the unit, that is to say, by the transfer of heat from the conditioning air through theintermediate wall 66 and out to atmosphere to the exhaust stack 12. A portion of this sensible heat load may also be taken by the expansion process.

Taking another set of conditions, such as the combination of high temperature and high relative humidity, most of the cooling load will initially be taken by the moisture removing processes (air expansion in the second chamber) since the evaporative cooling portion can deal only with the sensible heat load. When the relt 6 ative humidity has been lowered sufficiently in the conditioned space, the evaporative cooling action will then begin to take over, since it is now receiving air of lower relative humidity from the conditioning space and is now able to take on moisture for the evaporative cooling action to begin. The apparatus of this invention can therefore be described as self-generating in this respect.

Fundamentally, the conditioning air stream passing through chamber and the outgoing air stream pass-' ing through chamber 64, flow essentially in opposite directions in annular spaces formed between surfaces of revolution. in the particular example shown, the surfaces of revolution are conically shaped. However, it is not intended to restrict the configuration of the surfaces of revolution to that of a cone since it is quite possible that variations in the use of this apparatus may call for pressure and flow parameters only obtained by surfaces of revolution (or combinations of such) having other configurations than that of a cone. However, by employing the use of surfaces of revolution, the advantages become evident from both a manufacturing and a design standpoint when compared to a conventional multi-celular device which is used for the same basic purposes of heat exchange.

It is to be noted that the conditioned air upon being emitted from the outlet 78, is emitted in an annular configuration and substantially horizontal and would normally be emitted from the roof or top area of the conditioned space. As a result, the cooled air, being heavier, percolates downward to produce an entrainment effect with the stale air in a more or less gentle manner. In other words, there is no direct impingement upon the personnel within the conditioned space with the cool air. The warmer air is displaced upward directly adjacent the roof of the buillding and is brought into the unit through the inlet 16. Also, a portion of the warm air is caused to be supplied through inlet 14.

Although the apparatus 10 of this invention is described primarily as a cooling apparatus, it is feasible to employ such as a combined heating and cooling unit. It is contemplated that either gas or electric heating systems could be employed in combination with the apparatus.

lf gas heating is to be employed, it is envisioned that a gas heating unit would be located within the cooling plenum 54. As a result, the air which would be conducted through the chamber 64 would be of a high temperature. In essence, the opposite action which would then occur would be the heat energy being transferred from the chamber 64 into the chamber 80 resulting in a warming of the air passing therethrough. The flue gas which is produced by the gas heating unit would be carried to the ambient through the exhaust stack 12 and not be intermixed with the conditioned air. Draft reduction flaps can be installed adjacent the fan blades 50 to reduce the quantity of air passing through the first chamber 64. This is desirable with the apparatus employed as a heating unit. The flaps are to be set automatically when the unit is switched to the heating mode. If electrical heating elements are to be employed, they can be mounted directly within the inlet to the first chamber 64.

it may be desirable to include a means of humidification in combination with the apparatus 10 of this invention when operated as a heater. One way in which this can be accomplished is that in response to a humid ity sensor (not shown), water from the reservoir 88 can be diverted from the pump 36, which can lead to another spray ring, not shown, located adjacent the exit area of the second chamber 80. The water is then sprayed into the chamber prior to being conducted through the inlet 78. The unevaporated water may then be removed from this area by a conduit means and supplied back into the reservoir 88. The valve (not shown) controlling this flow of water would be automatically shut off on command from the sensor when the relative humidity in the conditioned space reached the desired level.

when the apparatus 10 is operating as a heating unit. it is noted that some heating of the water within the reservoir 88 is expected to occur due to its proximity to the heat source. This will aid in the vaporization of the humidifier spray water to improve the response time and economy of the operation of both the humidifier and the apparatus itself.

The apparatus of this invention is envisioned to be particularly adaptable within a wide variety of locations some of which are described as follows:

1. Industrial Use The unit of this invention may be suspended from roof supports within a factory above a machine shop area with the exhaust stack 12 being passed out through the roof of the factory. In this arrangement the apparatus is designed to operate as a free blowingdevice. Also, the apparatus of this invention may be installed upon a plant factory roof with ducting leading from inside the conditioned space to the apparatus of this inventron.

2. Mobile Homes and Low-Cost Housing Installation With this type of installation, the unit could be installed as a free blowing unit within the ceiling of the dwelling space. The upper part of the unit would be accessible from the roof, with the impeller fan outlet protruding into the dwelling space. Such a unit is shown in FIG. of the drawings with the apparatus l0 of this invention being mounted within the roof 102 of the dwelling space. Basically, the apparatus operates in a manner similar to the apparatus 10 with like numerals referring to like elements within the apparatus. However, an outer shroud 104 is employed to conduct the conditioned air through an inlet 106 into the inlet of the chamber 80.In this way the air for reconditioning is drawn directly off the walls and the ceiling of the dwelling space, passing through the unit and back into the conditioned space by way of the impeller outlet 78.

3. Single Family Dwelling Installation The appara' tus ofthis invention may be mounted in such an installation as a fully ducted unit upon the roof or inside the attic or roof space ofa single family dwelling. lfdesired, the air for the operation of the evaporative cooling system which is conducted through the chamber 64 may be drawn from inside the roof space itself. In this way, the air within the dwelling space would just be recirculated, not requiring the bringing in of additional air other than make-up" air, to be supplied through a standard vent.

I claim:

1. An air conditioning apparatus to condition air within a conditioned space, said apparatus comprising:

first air inlet means adapted to receive a first quantity of air from said conditioned space;

first chamber means adapted to receive said first quantity of air and conduct such to a first outlet, said first chamber means converges in direction of air flow resulting in the area of said first outlet being less than the area of said inlet of said first chamber means, said first outlet communicating with the ambient;

second air inlet means adapted to receive a second quantity of air from said conditioned space;

second chamber means adapted to receive said second quantity of air andconduct such to a second outlet, said first chamber means diverges in direction of air flow resulting in the area of said second outlet being greater than the area of said inlet of said second chamber means, said second chamber located directly adjacent said first chamber and adapted to exchange heat therebetween, said second outlet communicating with said conditioned space;

supply means to supply a liquid into said first chamber adjacent its inlet;

power means to conduct air into said first chamber and said second chamber; and the direction of the air flow through said second chamber being oppositeto the direction of the air flow through said first chamber.

2. Apparatus as defined in claim 1 wherein:

the outer wall of said first chamber comprising the inner wall of said second chamber.

3. Apparatus as defined in claim 2 wherein:

each of said first and second chamber means being configured in an annular space formed between surfaces of revolution.

4. Apparatus as defined in claim 3 wherein:

each of said surfaces of revolution comprising a conev 5. Apparatus as defined in claim 1 wherein:

said supply means comprises a device to spray said liquid, said liquid comprises water.

6. Apparatus as defined in claim 1 wherein:

said power means includes a compound air mover comprising a propeller fan to conduct air through the said first chamber and an impeller type fan to conduct the air through the said second chamber.

7. Apparatus as defined in claim 1 wherein:

said first quantity of air being of a substantially less volume than said second quantity of air.

8. In an air conditioning apparatus, a heat transfer means comprising:

a first chamber having a first inlet and a first outlet, said first chamber means converges in direction of air flow resulting in the area of said first outlet being less than the area of said first inlet, said first inlet adapted to receive a first quantity of air from a conditioned space, said first outlet to conduct air into the ambient, said first chamber formed into an annular space between surfaces of revolution;

a second chamber having a second inlet and a second outlet, said first chamber means diverges in direction of air flow resulting in the area of said second outlet being greater than the area of said second inlet, said second inlet adapted to receive a second quantity of air from a conditioned space, said second outlet to return air to the conditioned space,

said second chamber formed into an annular space between surfaces of revolution, said first chamber and said second chamber having a common surface of revolution to thereby effect heat transfer therebetween; and

the direction of the air flow through said second chamber being opposite the direction of the air flow through said first chamber.

9. Apparatus as defined in claim 8 wherein:

each of said surfaces of revolution comprises a cone.

[0. Apparatus as defined in claim 8 wherein:

said first quantity ofair being of substantially less volume than said second quantity of air.

11. Apparatus as defined in claim 8 including:

supply means located within said first chamber adjacent said first inlet to supply a liquid into said first chamber.

12. Apparatus as defined in claim 11 wherein:

said supply means comprises a device to spray said liquid, said liquid comprises water.

13. Apparatus as defined in claim 8 including:

power means to conduct air into said first chamber and said second chamber.

14. Apparatus as defined in claim 13 wherein:

said power means includes a compound air mover comprising a propeller fan to conduct air through 10 the said first chamber and an impeller type fan to conduct the air through the said second chamber.

15. Apparatus as defined in claim 1 wherein:

said first outlet connected to a moisture receiving plenum with said first outlet to discharge into said moisture receiving plenum, a portion of said liquid to condense within said moisture receiving plenum and then flow into a supply reservoir for recirculation.

16. Apparatus as defined in claim 12 wherein:

said first outlet connected to a moisture receiving plenum with said first outlet to discharge into said moisture receiving plenum, a portion of said liquid to condense within said moisture receiving plenum and then flow into a supply reservoir for recirculation.

17. Apparatus as defined in claim 15 wherein:

said condensed portion of water flows along an interior wall of said first chamber means to be conducted into said supply reservoir.

18. Apparatus as defined in claim 16 wherein:

said condensed portion of water flows along an interior wall of said first chamber means to be conducted into said supply reservoir.

l r l l 

1. An air conditioning apparatus to condition air within a conditioned space, said apparatus comprising: first air inlet means adapted to receive a first quantity of air from said conditioned space; first chamber means adapted to receive said first quantity of air and conduct such to a first outlet, said first chamber means converges in direction of air flow resulting in the area of said first outlet being less than the area of said inlet of said first chamber means, said first outlet communicating with the ambient; second air inlet means adapted to receive a second quantity of air from said conditioned space; second chamber means adapted to receive said second quantity of air and conduct such to a second outlet, said first chamber means diverges in direction of air flow resulting in the area of said second outlet being greater than the area of said inlet of said second chamber means, said second chamber located directly adjacent said first chamber and adapted to exchange heat therebetween, said second outlet communicating with said conditioned space; supply means to supply a liquid into said first chamber adjacent its inlet; power means to conduct air into said first chamber and said second chamber; and the direction of the air flow through said second chamber being opposite to the direction of the air flow through said first chamber.
 2. Apparatus as defined in claim 1 wherein: the outer wall of said first chamber comprising the inner wall of said second chamber.
 3. Apparatus as defined in claim 2 wherein: each of said first and second chamber means being configured in an annular space formed between surfaces of revolution.
 4. Apparatus as defined in claim 3 wherein: each of said surfaces of revolution comprising a cone.
 5. Apparatus as defined in claim 1 wherein: said supply means comprises a device to spray said liquid, said liquid comprises water.
 6. Apparatus as defined in claim 1 wherein: said power means includes a compound air mover comprising a propeller fan to conduct air through the said first chamber and an impeller type fan to conduct the air through the said second chamber.
 7. Apparatus as defined in claim 1 wherein: said first quantity of air being of a substantially less volume than said second quantity of air.
 8. In an air conditioning apparatus, a heat transfer means comprising: a first chamber having a first inlet and a first outlet, said first chamber means converges in direction of air flow resulting in the area of said first outlet being less than the area of said first inlet, said first inlet adapted to receive a first quantity of air from a conditioned space, said first outlet to conduct air into the ambient, said first chamber formed into an annular space between surfaces of revolution; a second chamber having a second inlet and a second outlet, said first chamber means diverges in direction of air flow resulting in the area of said second outlet being greater than the area of said second inlet, said second inlet adapted to receive a second quantity of air from a conditioned space, said second outlet to return air to the conditioned space, said second chamber formed into an annular space between surfaces of revolution, said first chamber and said second chamber having a common surface of revolution to thereby effect heat transfer therebetwEen; and the direction of the air flow through said second chamber being opposite the direction of the air flow through said first chamber.
 9. Apparatus as defined in claim 8 wherein: each of said surfaces of revolution comprises a cone.
 10. Apparatus as defined in claim 8 wherein: said first quantity of air being of substantially less volume than said second quantity of air.
 11. Apparatus as defined in claim 8 including: supply means located within said first chamber adjacent said first inlet to supply a liquid into said first chamber.
 12. Apparatus as defined in claim 11 wherein: said supply means comprises a device to spray said liquid, said liquid comprises water.
 13. Apparatus as defined in claim 8 including: power means to conduct air into said first chamber and said second chamber.
 14. Apparatus as defined in claim 13 wherein: said power means includes a compound air mover comprising a propeller fan to conduct air through the said first chamber and an impeller type fan to conduct the air through the said second chamber.
 15. Apparatus as defined in claim 1 wherein: said first outlet connected to a moisture receiving plenum with said first outlet to discharge into said moisture receiving plenum, a portion of said liquid to condense within said moisture receiving plenum and then flow into a supply reservoir for recirculation.
 16. Apparatus as defined in claim 12 wherein: said first outlet connected to a moisture receiving plenum with said first outlet to discharge into said moisture receiving plenum, a portion of said liquid to condense within said moisture receiving plenum and then flow into a supply reservoir for recirculation.
 17. Apparatus as defined in claim 15 wherein: said condensed portion of water flows along an interior wall of said first chamber means to be conducted into said supply reservoir.
 18. Apparatus as defined in claim 16 wherein: said condensed portion of water flows along an interior wall of said first chamber means to be conducted into said supply reservoir. 